CN112041585B - Damping force generating mechanism and pressure shock absorber - Google Patents

Damping force generating mechanism and pressure shock absorber Download PDF

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Publication number
CN112041585B
CN112041585B CN201980027719.5A CN201980027719A CN112041585B CN 112041585 B CN112041585 B CN 112041585B CN 201980027719 A CN201980027719 A CN 201980027719A CN 112041585 B CN112041585 B CN 112041585B
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China
Prior art keywords
flow passage
seat
valve
main valve
oil
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CN201980027719.5A
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CN112041585A (en
Inventor
中野刚太
柳泽力
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Hitachi Astemo Ltd
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Hitachi Astemo Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/185—Bitubular units
    • F16F9/187—Bitubular units with uni-directional flow of damping fluid through the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/185—Bitubular units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3484—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of the annular discs per se, singularly or in combination
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3485—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of supporting elements intended to guide or limit the movement of the annular discs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F16F9/464—Control of valve bias or pre-stress, e.g. electromagnetically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/516—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics resulting in the damping effects during contraction being different from the damping effects during extension, i.e. responsive to the direction of movement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
    • B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
    • B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/06—Characteristics of dampers, e.g. mechanical dampers
    • B60G17/08—Characteristics of fluid dampers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/20—Type of damper
    • B60G2202/24—Fluid damper
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
    • B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
    • B60G2206/40—Constructional features of dampers and/or springs
    • B60G2206/41—Dampers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2500/00—Indexing codes relating to the regulated action or device
    • B60G2500/10—Damping action or damper
    • B60G2500/11—Damping valves
    • B60G2500/114—Damping valves pressure regulating valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
    • B60G2800/16—Running
    • B60G2800/162—Reducing road induced vibrations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/025—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant characterised by having a particular shape
    • F16F1/027—Planar, e.g. in sheet form; leaf springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/12—Fluid damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2226/00—Manufacturing; Treatments
    • F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
    • F16F2228/06—Stiffness
    • F16F2228/066—Variable stiffness
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2232/00—Nature of movement
    • F16F2232/08—Linear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2234/00—Shape
    • F16F2234/02—Shape cylindrical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • F16F9/5126—Piston, or piston-like valve elements

Abstract

The damping force generating mechanism includes: a flow passage forming part which forms a flow passage through which liquid flows; and a valve controlling the flow of the liquid in the flow passage. The flow passage forming part includes: a first seat portion formed radially outward of the flow passage inlet, and protruding from the flow passage inlet and coming into contact with the valve; a second seat portion provided radially outside the first seat portion, protruding from the flow passage inlet and coming into contact with the valve; and a circulation portion having an orifice through which liquid can circulate from the flow passage inlet toward the second seat portion while the valve is in a state of being in contact with the first seat portion.

Description

Damping force generating mechanism and pressure shock absorber
Technical Field
The present invention relates to a damping force generating mechanism and a pressure shock absorber.
Background
For example, patent document 1 discloses a simple support structure in which a main valve has an inner peripheral portion that is sandwiched not from both surface sides but from a non-valve seat portion side on the inner peripheral side and is sandwiched between the main valve and an outer valve seat portion, and in which a cut valve having an inner peripheral portion sandwiched from both surface sides and having a coupling portion with low rigidity formed between the outer peripheral portion and the inner peripheral portion is provided, so that a damping force generated by the cut portion (fixed orifice) of the cut valve is obtained before the main valve opens, and the main valve can be opened with a small differential pressure using the simple support structure.
Patent document 1: JP 2017-48825A
Disclosure of Invention
However, in the case where a valve is provided on a flow passage of liquid to generate a damping force, the characteristics of the generated damping force depend on the valve opening characteristics of the valve. Here, the device may be complicated when the number of components involved in opening the valve is increased to obtain a desired damping force characteristic.
The purpose of the present invention is to obtain a desired damping force characteristic while simplifying a structure relating to the valve opening characteristic of a valve.
According to an aspect of the present invention, there is provided a damping-force generating mechanism including: a flow path forming part forming a flow path through which a liquid flows; and a valve configured to control a flow of the liquid within the flow passage, wherein the flow passage forming part includes: a first seat formed radially outside a flow passage port of the flow passage, protruding from the flow passage port, and contacting the valve; a second seat that is disposed further radially outward than the first seat, protrudes from the flow passage port, and contacts the valve; and a circulation portion having an orifice that enables the liquid to flow from the flow passage port toward the second seat in a state where the valve is in contact with the first seat.
Advantageous effects of the invention
According to the present invention, a desired damping force characteristic can be obtained while simplifying the structure relating to the valve opening characteristic of the valve.
Drawings
Fig. 1 is an overall view of a hydraulic shock absorber according to a first embodiment.
Fig. 2 is a sectional view of an outer damping portion according to the first embodiment.
Fig. 3 is a perspective sectional view of the main valve portion and the damping force adjusting portion according to the first embodiment.
Fig. 4 is a partial sectional view of the main valve portion and the damping force adjusting portion according to the first embodiment.
Fig. 5 is a top view of a main valve seat according to a first embodiment.
Fig. 6A and 6B are explanatory diagrams of a control valve and a control valve seat according to the first embodiment.
Fig. 7A and 7B are explanatory diagrams showing the operation of the hydraulic shock absorber according to the first embodiment.
Fig. 8A and 8B are explanatory diagrams of the flow of oil in the outer damping portion according to the first embodiment.
Fig. 9A and 9B are explanatory diagrams of the flow of oil in the outer damping portion according to the first embodiment.
Fig. 10A and 10B are explanatory diagrams of the flow of oil in the outer damping portion according to the first embodiment.
Fig. 11 is an explanatory diagram of the damping force characteristic of the main valve portion according to the first embodiment.
Fig. 12A and 12B are explanatory diagrams of a hydraulic shock absorber according to a first modification.
Fig. 13 is an explanatory diagram of a hydraulic damper 1 according to a second modification.
Fig. 14 is a sectional view of an outer damping portion according to a second embodiment.
Fig. 15 is a partial sectional view of the main valve portion and the damping force adjusting portion according to the second embodiment.
Fig. 16 is an explanatory diagram of a main valve seat according to the second embodiment.
Fig. 17 is an explanatory view of a back pressure forming portion according to the second embodiment.
Fig. 18 is an explanatory diagram of a hydraulic damper according to a third modification.
List of reference marks
1 Hydraulic shock absorber
11 cylinder body
20 bar
30 piston part
50 main valve part
51 main valve
52 main valve seat
53 main runner
60 damping force adjusting part
65 pressing part
67 cover part
68 backpressure generating mechanism
68P back pressure chamber
70 control valve
75 control valve seat
100 outer damping part
521 inner seat part
522 outer seat part
681 partition wall member
682 seal member
683 reset spring
Detailed Description
Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
< first embodiment >
[ construction and action of Hydraulic shock absorber 1 ]
Fig. 1 is an overall view of a hydraulic shock absorber 1 according to a first embodiment.
As shown in fig. 1, the hydraulic shock absorber 1 includes: a cylinder section 10 for containing oil; and a rod 20 provided with one side slidably inserted into the cylinder 10 and the other side protruding from the cylinder 10. In addition, the hydraulic shock absorber 1 includes: a piston portion 30, the piston portion 30 being provided at an end portion on one side of the rod 20; and a bottom portion 40 provided at an end portion on one side of the cylinder portion 10. Further, the hydraulic shock absorber 1 includes an outer damping portion 100, and the outer damping portion 100 is disposed outside the cylinder portion 10 to generate a damping force.
In the following description, the longitudinal direction of the cylinder portion 10 shown in fig. 1 is referred to as "axial direction". The lower side of the cylinder portion 10 in the axial direction is referred to as "one side", and the upper side of the cylinder portion 10 is referred to as "the other side".
The left-right direction of the cylinder portion 10 shown in fig. 1 is referred to as a "radial direction". Further, in the radial direction, the central axis side is referred to as "radially inner side", and the side away from the central axis is referred to as "radially outer side".
[ construction and action of the cylinder section 10 ]
The cylinder section 10 includes: a cylinder 11 for containing oil; an outer tubular body 12 provided radially outside the cylinder block 11; and a damper housing 13 provided radially outside the cylinder block 11 and also radially outside the outer tubular body 12.
The cylinder 11 is formed in a cylindrical shape, and includes a cylinder opening 11H on the other side.
The outer tubular body 12 is formed in a cylindrical shape. Further, the outer tubular body 12 forms a communication passage L with the cylinder 11. In addition, the outer tubular body 12 has an outer tubular body opening portion 12H and an outer connecting portion 12J at a position facing the outer damper portion 100. The outer connection portion 12J has an oil flow passage, and protrudes radially outward to form a connection portion with the outer damping portion 100.
The damper housing 13 is formed in a cylindrical shape. The damper housing 13 forms a reservoir chamber R in which oil accumulates between the damper housing 13 and the outer tubular body 12. The reserve chamber R absorbs the oil in the cylinder 11 and supplies the oil to the inside of the cylinder 11 as the rod 20 moves relative to the cylinder 11. In addition, the reservoir chamber R stores the oil flowing out from the outer damping portion 100. The damper housing 13 includes a housing opening portion 13H at a position facing the outer damper portion 100.
[ construction and action of the rod 20 ]
The rod 20 is a rod-shaped member extending in the axial direction. One side of the rod 20 is connected to the piston portion 30. The other side of the rod 20 is connected to the vehicle body via a connecting member (not shown), for example. The rod 20 may have a hollow shape with a hollow inside or a solid shape without a cavity formed inside.
[ construction and action of the piston portion 30 ]
The piston portion 30 includes: a piston body 31 having a plurality of piston oil ports 311; a piston valve 32 for opening and closing the other side of the piston oil port 311; and a spring 33 provided between the piston valve 32 and an end portion on one side of the rod 20. Further, the piston section 30 divides the oil in the cylinder block 11 into the first oil chamber Y1 and the second oil chamber Y2.
[ constitution and action of bottom part 40 ]
The bottom portion 40 includes: a valve seat 41; a check valve portion 43 provided on the other side of the valve seat 41; and a fixing member 44 disposed in the axial direction. Further, the bottom portion 40 separates the first oil chamber Y1 and the reservoir chamber R from each other.
[ construction and action of outer damper portion 100 ]
Fig. 2 is a sectional view of the outer damping portion 100 according to the first embodiment.
Fig. 3 is a perspective sectional view of the main valve portion 50 and the damping force adjusting portion 60 according to the first embodiment.
Fig. 4 is a partial sectional view of the main valve portion 50 and the damping force adjusting portion 60 according to the first embodiment.
Fig. 5 is a top view of the main valve seat 52 according to the first embodiment.
In the following description, the length direction of the outer damping portion 100 shown in fig. 2, that is, the intersecting direction (e.g., a substantially orthogonal direction) that intersects the axial direction of the cylinder portion 10 (see fig. 1) is referred to as "second axial direction". In addition, the left side of the outer damping portion 100 in the second axial direction is referred to as "second axially inner side", and the right side of the outer damping portion 100 is referred to as "second axially outer side".
The up-down direction of the outer damping portion 100 shown in fig. 2 (i.e., the direction intersecting the second axial direction) is referred to as "second radial direction". Further, in the second radial direction, the central axis side along the second axis is referred to as "second radial inner side", and the side away from the central axis along the second axis is referred to as "second radial outer side".
As shown in fig. 2, the outer damping portion 100 includes: a main valve portion 50 that generates a damping force mainly in the hydraulic shock absorber 1 according to the first embodiment; and a damping force adjusting part 60 that adjusts the magnitude of the damping force generated by the outer damping part 100. Further, the outer damping portion 100 includes: a communication portion 80 that forms a parallel flow passage with respect to the main valve portion 50; a connection flow passage portion 90 that forms a flow passage for oil from the communication passage L for the main valve portion 50 and the communication portion 80; and an outer case 100C that accommodates various components constituting the outer damping portion 100.
(Main valve portion 50)
The main valve portion 50 includes: a main valve 51 that generates a damping force by controlling the flow of oil to be throttled; and a main valve seat 52 (an example of a flow passage forming portion) that faces the main valve 51 and makes contact with the main valve 51.
As shown in fig. 3, the main valve 51 is a disk-shaped member that has an opening portion 51H on the second radially inner side and is elastically deformed. For example, a metal such as iron may be used as the material of the main valve 51.
As shown in fig. 4, the communication portion 80 penetrates the opening 51H of the main valve 51. In addition, a second radially inner side of the main valve 51 is interposed between the main valve seat 52 and a washer member 684 (described later). Further, the main valve 51 faces the second axially outer side of the main valve seat 52.
The communication portion 80 restricts the position of the main valve 51 configured as described above from moving in the second radial direction. In addition, the second radially inner side of the main valve 51 is restricted from moving in the second axial direction by the main valve seat 52 and a washer member 684 (described later). On the other hand, the second radially outer side of the main valve 51 is deformable to be movable in the second axial direction. Further, the main valve 51 throttles the flow of oil in a later-described main flow passage 53 of the main valve seat 52 to generate a damping force.
Next, the main valve seat 52 will be described.
As shown in fig. 3, the main valve seat 52 is a columnar member having an opening 52H on the second radial direction inner side. Further, the communication portion 80 is inserted into a part of the opening portion 52H of the main valve seat 52 (see fig. 4).
As shown in fig. 5, the main valve seat 52 includes a center seat portion 520 around the opening portion 52H. In addition, the main valve seat 52 includes: an inner seat 521 (an example of a first seat) disposed on a second radially outer side of the center seat 520; and an outer seat portion 522 (an example of a second seat portion) disposed on a second radially outer side of the inner seat portion 521. Further, the main valve seat 52 includes a main flow passage 53 penetrating in the second axial direction on the second radial direction outer side of the opening portion 52H.
The center seat portion 520 protrudes in an arc toward the main valve 51 (the second axial outer side in the present embodiment). Furthermore, a second radially inner portion of the main valve 51 faces the central seat 520.
The inner seat portion 521 is formed in an annular shape. The inner seat portion 521 protrudes from the port opening 532 toward the main valve 51. In addition, in the first embodiment, the protruding height of the inner seat 521 is substantially equal to the protruding height of the center seat 520 and the outer seat 522.
The outer seat portion 522 is formed in an annular shape. Further, the outer seat portion 522 protrudes from the port hole 532 toward the main valve 51 side.
The inner seat 521 and the outer seat 522 form a contact portion with the main valve 51 (see fig. 4).
The inner seat 521 according to the first embodiment has a plurality of groove portions 521T (an example of a circulating portion) formed along the second radial direction. The cross-sectional area of the flow path of each groove 521T is formed to be relatively small. That is, the groove portion 521T constitutes a so-called orifice flow passage. Further, each groove portion 521T forms a path for flowing oil from the second radial direction inner side of the inner seat portion 521 to the second radial direction outer side of the inner seat portion 521 in a state where the main valve 51 is in contact with the inner seat portion 521. That is, when the main valve 51 comes into contact with the inner seat 521, the grooves 521T allow oil from the main flow passage 53 to flow between the inner seat 521 and the outer seat 522.
The main flow passage 53 forms a parallel flow passage of a back pressure flow passage 77 and a low speed flow passage 78 described later with respect to the control valve seat 75. A plurality of primary flow channels 53 according to the first embodiment are provided (see fig. 5). The second axially inner flow channel port 531 of each main flow channel 53 communicates with the opening 52H and faces the connecting flow channel portion 90. Further, a second axially outer flow port 532 (an example of a flow port) of each main flow passage 53 is located between the center seat 520 and the inner seat 521.
(damping force adjusting part 60)
As shown in fig. 3, the damping force adjusting portion 60 includes: an advancing and retreating portion 61 that advances and retreats a control valve 70 described later with respect to a control valve seat 75; a lid portion 67 that covers various components such as the main valve portion 50; and a back pressure generating mechanism 68 that changes the ease of deformation of the main valve 51 with respect to the main valve seat 52. In addition, the damping force adjusting portion 60 includes: a control valve 70 that throttles and controls the flow of oil in the communication portion 80; a control valve seat 75 facing the control valve 70 and making contact with the control valve 70; and a throttle member 79 that throttles the flow of oil.
Advancing and retreating section 61-
As shown in fig. 2, the advancing and retreating section 61 includes: a solenoid portion 62 that electromagnetically advances and retreats a plug 64; a compression coil spring 63 provided between the pressurizing member 65 and the control valve 70; a plug 64 that advances and retreats in the second axial direction; and a pressing member 65 that presses the control valve 70 against the control valve seat 75. In addition, the advancing and retreating portion 61 includes a solenoid case 60C that houses and supports the members constituting the advancing and retreating portion 61.
When electromagnetically energized, the solenoid portion 62 pushes the plug 64 toward the pressing member 65 side.
The compression coil spring 63 contacts the control valve 70 on the second axial inner side, and contacts the pressing member 65 on the second axial outer side. Further, the compression coil spring 63 applies a force in a direction to separate the pressurizing member 65 and the control valve 70 from each other to the pressurizing member 65 and the control valve 70, respectively.
When the solenoid portion 62 is in an energized state, the plug 64 is pushed out toward the pressing member 65, and when the solenoid portion 62 is in an un-energized state, the plug 64 is pulled back by the compression coil spring 63.
As shown in fig. 3, the pressing member 65 includes a valve contact portion 651 that protrudes toward the control valve 70 (toward the second axial inner side). The valve contact portion 651 according to the first embodiment is formed in an annular shape. Further, a valve contact portion 651 is formed at a position facing a second facing portion 72 (described later, see fig. 6A and 6B) of the control valve 70. The valve contact portion 651 contacts the second facing portion 72.
The pressing member 65 (an example of a pressing portion) includes a groove 653 (an example of a groove) on the second axial outer side. The groove portion 653 allows oil to flow between the pressing member 65 and the lid portion 67 in a state where the pressing member 65 moves axially outward and comes into contact with the lid portion 67.
In the first embodiment, the flow passage sectional area of the oil in the groove portion 653 is set to: when the solenoid portion 62 (an example of an operating portion) is in an unexcited state, the oil pressure of the back pressure chamber 68P, which will be described later, is increased to be constant or higher. Further, the flow passage sectional area of the oil in the groove portion 653 is set to: when the solenoid portion 62 (an example of an operating portion) is in an unexcited state, oil flows through this groove portion 653 to such an extent that the main valve 51 opens the main flow passage 53 to allow the oil to flow.
The configuration of the flow of oil between the cap 67 and the pressing member 65 when the solenoid portion 62 is in the non-excited state is not limited to the groove portion 653. For example, by providing a groove portion in the lid portion 67, the flow of oil between the pressing member 65 and the lid portion 67 can be made possible in a state where the pressing member 65 and the lid portion 67 come into contact. The groove portion may be formed in the lid portion 67, and the groove portion 653 may be provided in the pressing member 65. Further, the configuration that causes the oil to flow between the cover 67 and the pressing member 65 in the state where the pressing member 65 comes into contact with the cover 67 is not limited to the groove portion, and may be a through hole.
A cap 67-
As shown in fig. 3, the lid portion 67 includes a first opening portion 67H1 formed on the second axially inner side and a second opening portion 67H2 formed on the second axially outer side, and is a member having a substantially cylindrical shape. In addition, the first inner diameter of the first opening portion 67H1 is larger than the second inner diameter of the second opening portion 67H 2. Further, a plurality of inner diameter portions having different inner diameters are formed inside the lid portion 67. In the lid portion 67 according to the first embodiment, an inner diameter portion disposed on the second axial inner side among the plurality of inner diameter portions is formed to have a larger inner diameter than an inner diameter portion disposed on the second axial outer side.
As shown in fig. 4, the main valve portion 50, the damping force adjustment portion 60, and the communication portion 80 are accommodated in the cover portion 67 (an example of an accommodating portion). More specifically, the cap portion 67 accommodates a main valve 51 (an example of a valve) of the main valve portion 50 and a control valve 70 (an example of a back pressure control valve) for controlling back pressure of a back pressure chamber 68P (described later) in the damping force adjustment portion 60. In addition, as will be described later, a part of the lid portion 67 forms a back pressure chamber 68P together with the back pressure generating mechanism 68 and a control valve seat 75.
The lid portion 67 is provided with a plug 64 penetrating the second opening portion 67H 2. In addition, in the lid portion 67, the pressing member 65 moves forward and backward with respect to the second opening portion 67H2 inside the lid portion 67.
As shown in fig. 2, the lid portion 67 is fixed by being sandwiched between the solenoid case 60C and the connection flow path portion 90. Further, the lid portion 67 forms a lid flow passage 67R, and oil flows between the lid portion 67 and the solenoid case 60C through the lid flow passage 67R. The lid flow passage 67R communicates with the second opening portion 67H2, and also communicates with an in-case flow passage 111, which will be described later.
Back pressure generating means 68
As shown in fig. 3, the back pressure generating mechanism 68 includes: a partition wall member 681 (an example of a back pressure chamber forming portion) provided on the opposite side of the main valve 51 from the main valve seat 52 (i.e., the second axially outer side); and a seal member 682 that seals (i.e., is liquid-tight) between the lid portion 67 and the partition wall member 681. Further, the back pressure generating mechanism 68 includes: a return spring 683 that applies a force to the partition wall member 681 to press the partition wall member 681 against the main valve 51; and a washer member 684 interposed between the return spring 683 and the main valve 51.
The partition wall 681 is formed in a substantially annular shape. As shown in fig. 4, a clearance C1 in the second radial direction is formed between the partition wall member 681 and the lid portion 67. Further, the partition wall member 681 is movable in the second axial direction. For example, when the main valve 51 deforms axially outward, the partition wall member 681 moves axially outward. When the main valve 51 deforms inward in the second axis direction, the partition wall member 681 moves inward in the second axis direction.
The partition wall portion 681 according to the first embodiment includes: a main valve contact portion 681V that contacts the main valve 51; and a seal contact portion 681S in which the seal member 682 is provided.
A main valve contact portion 681V (an example of a contact portion) is provided at the second axially inner side of the partition wall member 681. The main valve contact portion 681V according to the first embodiment is formed such that the width gradually decreases from the second outward side to the second inward side. The main valve contact portion 681V contacts the main valve 51 in an annular shape. Further, the partition wall member 681 constitutes one of members forming a back pressure chamber 68P, and the back pressure chamber 68P causes an oil pressure (hereinafter, referred to as back pressure) from a second axially outer side opposite to the main valve seat 52 to act on the main valve 51.
Here, the back pressure chamber 68P is a chamber: the oil flows into back pressure chamber 68P, and the oil pressure corresponding to the inflow oil acts on main valve 51. The back pressure chamber 68P acts on the main valve 51, and applies a force that presses the main valve 51 against the main valve seat 52. Incidentally, the back pressure chamber 68P according to the first embodiment is formed by the lid portion 67, the partition wall member 681, the seal member 682, the gasket member 684, and the control valve seat 75.
As shown in fig. 4, the main valve contact portion 681V contacts the main valve 51 at the second radial direction portion of the main valve 51. As a result, the back pressure is applied to the main valve 51 in the second radial direction ranging from the end of the washer member 684 on the second radial direction outer side to the main valve contact portion 681V. That is, the back pressure is not applied to the second axially outer side of the main valve contact portion 681V of the main valve 51.
In the first embodiment, the main valve contact portion 681V makes contact with the main valve 51 on the second radial direction outer side of the facing portion of the inner seat portion 521 and on the second radial direction inner side of the facing portion of the outer seat portion 522.
Here, when the main flow passage 53 is opened, the main valve 51 is opened from the second radial outside. Further, the outer damping portion 100 according to the first embodiment is configured such that the main valve contact portion 681V makes contact with the second radially inner side of the facing portion of the outer seat portion 522. Therefore, the outer damping portion 100 according to the first embodiment has a structure in which: the ease of deformation of the main valve 51 when the main valve 51 is separated from the outer seat portion 522 due to the flow of oil from the main flow passage 53 can be adjusted. That is, the outer damping portion 100 according to the first embodiment includes the main valve contact portion 681V, so that the damping force characteristic generated by the main valve 51 can be adjusted.
The partition wall member 681 according to the first embodiment can easily adjust the ease of deformation of the main valve 51 by changing the contact position of the main valve contact portion 681V with respect to the main valve 51. As described above, the partition wall portion 681 according to the first embodiment is configured to improve the degree of freedom in design.
The seal contact portion 681S includes: a first surface S1, the first surface S1 being a second radially outward facing surface; and a second surface S2, the second surface S2 being a surface facing the second axially outward side.
The outer diameter of the first surface S1 is smaller than the inner diameter of the seal member 682. Therefore, in the first embodiment, the clearance C2 is formed between the inner circumferential surface 682N and the first surface S1 (outer circumferential surface) of the seal member 682.
In the first embodiment, the oil pressure in the backpressure chamber 68P is applied to the inner peripheral surface 682N of the seal member 682 by forming the clearance C2 between the inner peripheral surface 682N and the first surface S1. Further, in the first embodiment, the outer peripheral surface 682G of the seal member 682 is pressed against the inner peripheral surface of the cover portion 67 by the oil pressure applied to the inner peripheral surface 682N of the seal member 682.
The second surface S2 is a surface formed in an annular shape. Further, the end face 682T of the seal member 682 comes into contact with the second surface S2. Specifically, in the first embodiment, the end face 682T of the seal member 682 is pressed against the second face S2 of the partition wall member 681 by the return spring 683.
As shown in fig. 3, the seal member 682 is formed in an annular shape. In addition, an elastically deformable resin material such as engineering plastic or rubber can be used for the seal member 682.
Then, as shown in fig. 4, the seal member 682 seals between the partition wall member 681 and the lid portion 67. More specifically, an outer peripheral surface 682G of the seal member 682 comes into contact with the inner periphery of the lid portion 67. The second axially inner end face 682T of the seal member 682 contacts the second surface S2 of the partition wall member 681. Therefore, the seal member 682 prevents the oil in the back pressure chamber 68P from flowing out of the back pressure chamber 68P through the gap between the partition wall member 681 and the lid 67.
As shown in fig. 3, the return spring 683 includes: an annular portion 683R formed in an annular shape; and a plurality of arm portions 683A protruding to the second radially outer side from the annular portion 683R. In addition, an elastic member such as metal may be used as the material of the return spring 683.
As shown in fig. 4, in the return spring 683, the communicating portion 80 passes through the annular portion 683R, and the annular portion 683R is sandwiched by the plurality of washer members 684 in the second axial direction. In addition, the arm portion 683A of the return spring 683 contacts the seal member 682.
In the return spring 683 according to the first embodiment, the position at which the annular portion 683R is fixed by the washer member 684 and the position at which the arm portion 683A contacts the seal member 682 are different in the second axial direction. Each arm portion 683A has a shape inclined with respect to the second axial direction. Further, the arm 683A contacts a corner portion of the seal member 682 on the second radially inner side and the second axially outer side. Accordingly, the arm portion 683A applies an elastic force component in the second axial direction and an elastic force component in the second radial direction to the seal member 682.
First, the arm portion 683A of the return spring 683 applies a force toward the partition wall member 681 (an example of the back pressure chamber forming portion) of the back pressure generation mechanism 68 to the seal member 682 by a component force in the second axial direction. As a result, the return spring 683 presses the partitioning wall member 681 toward the main valve 51 via the seal member 682.
The arm portion 683A of the return spring 683 (an example of an elastic member) according to the first embodiment presses the seal member 682 (an example of a seal portion) toward the cover portion 67 (an example of a housing portion) by a component force in the second radial direction. As a result, in the first embodiment, the sealing performance between the sealing member 682 and the cover portion 67 is improved.
In the return spring 683 according to the first embodiment, the arm portion 683A also comes into contact with the partitioning wall member 681. Further, the return spring 683 applies a spring force component in the second axial direction and a spring force component in the second radial direction to the partition wall member 681.
First, the arm portion 683A presses the partitioning wall member 681 toward the main valve 51 by the elastic force component in the second axial direction.
Further, the arm portion 683A applies a force toward the second radial direction outer side to the partition wall member 681 by the elastic force component in the second radial direction. In the first embodiment, the plurality of arm portions 683A are provided in the circumferential direction (see fig. 3). Thus, the arm 683A positions the partitioning wall members 681 at predetermined positions in the second radial direction.
Control valve 70
Fig. 6A and 6B are explanatory diagrams of the control valve 70 and the control valve seat 75 according to the first embodiment.
As shown in fig. 6A, the control valve 70 is a substantially disc-shaped member that is elastically deformed. As the material of the control valve 70, for example, a metal such as iron may be used. The control valve 70 is disposed to face a control valve seat 75 (another example of the flow passage forming portion) on the second axial outer side.
Further, the control valve 70 (an example of a second valve) according to the first embodiment controls the flow of oil in the low-speed flow passage 78 (an example of another flow passage) and the back-pressure flow passage 77 (an example of another flow passage) that are parallel to and different from the main flow passage of the main valve portion 50.
The control valve 70 includes: an outer ring portion 70C formed in an annular shape; a first facing portion 71 facing the back pressure flow passage 77; and a second facing portion 72 that faces the low speed flow passage 78. Further, the control valve 70 includes: an inner opening portion 73 provided on the second radially inner side to facilitate deformation of the control valve 70 in the second axial direction; and an outer opening portion 74 provided radially outside the inner opening portion 73 to facilitate deformation of the control valve 70 in the second axial direction.
The outer ring portion 70C is disposed on the second radially outer side. Further, the outer ring portion 70C serves as a portion sandwiched between the cover portion 67 and the control valve seat 75. The control valve 70 according to the first embodiment is held by a control valve seat 75 by the sandwiched outer ring portion 70C (see fig. 4).
The first facing portion 71 has a circular shape, and is formed in a plate shape. The first facing portion 71 is formed larger than the inner diameter of the back pressure flow path 77 and can cover the back pressure flow path circle 77R. In the first embodiment, the first facing portion 71 is formed at the central portion (i.e., the second radially inner side) of the control valve 70.
The second facing portion 72 has an annular shape, and is formed in a plate shape. The second facing portion 72 is formed larger than the inner diameter of the low-speed flow passage 78 and can cover the low-speed flow passage circle 78R. The second facing portion 72 is formed on a second radially outer side of the first facing portion 71. In addition, the second facing portion 72 is formed as an annular region in the control valve 70. Therefore, in the first embodiment, the second facing portion 72 always faces the low-speed flow passage 78 regardless of the position of the control valve 70 in the circumferential direction with respect to the control valve seat 75.
The inner opening portion 73 is provided to extend long in the circumferential direction of the control valve 70. Further, a plurality of inner openings 73 are provided. Further, the inner arm portion 73A is formed between two adjacent inner opening portions 73. Each inner arm portion 73A is formed such that at least a part thereof extends in the circumferential direction. In the first embodiment, the plurality of inner arm portions 73A are formed in a spiral shape as a whole. In addition, in the control valve 70, the inner arm portion 73A is provided at the second radially outer side of the first facing portion 71 and at the second radially inner side of the second facing portion 72. That is, the inner arm portion 73A is provided between the first facing portion 71 and the second facing portion 72 in the second radial direction.
The width B11 of the inner arm portion 73A on the side closer to the first facing portion 71 is larger than the width B12 on the side farther from the first facing portion 71. Further, the width B13 of the inner arm portion 73A at the side closer to the second facing portion 72 is larger than the width B12 at the side farther from the second facing portion 72.
As shown in fig. 6A, the outer opening portion 74 is provided to extend in the circumferential direction of the control valve 70. A plurality of outer openings 74 are provided, and the plurality of outer openings 74 are provided at substantially equal intervals in the circumferential direction. Further, in the control valve 70 according to the first embodiment, the different two outer openings 74 are provided so as to overlap each other in the second radial direction.
As shown in fig. 6B, the outer opening 74 is formed at a second radially outer side of the second facing portion 72 and at a second radially inner side of the outer ring portion 70C.
The outer arm portion 74A is formed between adjacent two outer opening portions 74. Each outer arm portion 74A is formed such that at least a part thereof extends in the circumferential direction. In addition, in the first embodiment, the plurality of outer arm portions 74A are formed in a spiral shape as a whole. Further, in the control valve 70, the outer arm portion 74A is disposed at a second radially outer side of the second facing portion 72 and at a radially inner side of the outer ring portion 70C. That is, the outer arm portion 74A is disposed between the second facing portion 72 and the outer ring portion 70C in the second radial direction.
As shown in fig. 6A, in each outer opening 74, a width H1 of an inner region 741 formed at the second radially inner side of the outer arm portion 74A is larger than a width H2 of an outer region 742 formed at the second radially outer side of the outer arm portion 74A.
Further, the opening area of the outer opening portion 74 is maximized as compared with other openings formed in the control valve 70. In the first embodiment, the inner region 741 of the outer opening 74 constitutes a main flow passage of oil flowing through the control valve 70.
In the control valve 70 according to the first embodiment, the outer arm portion 74A is disposed on the second radial outside of the inner region 741 of the outer opening portion 74 having a large opening area. In the control valve 70 according to the first embodiment, when oil flows as described below, the flow rate of the second radially outer side is smaller than the flow rate of the second radially inner side. Therefore, in the first embodiment, the outer arm portion 74A is disposed outside the inner region 741 of the outer opening portion 74 in the second radial direction, so that the influence of the dynamic pressure of the oil flowing through the outer opening portion 74 is reduced for this outer arm portion 74A configured to have a lower rigidity.
Further, as shown in fig. 6B, the width B21 of the outer arm portion 74A at the side closer to the second facing portion 72 is larger than the width B22 at the side farther from the second facing portion 72. Further, the width B23 of the outer arm portion 74A at the side closer to the outer ring portion 70C is larger than the width B22 at the side farther from the outer ring portion 70C.
In the control valve 70 according to the first embodiment, the rigidity of the portions where the inner arm portion 73A and the outer arm portion 74A are formed is reduced, and the portions where the inner arm portion 73A and the outer arm portion 74A are formed are easily deformed. In particular, in the first embodiment, for example, the inner arm portion 73A and the outer arm portion 74A are formed to extend in the circumferential direction, respectively, the length of the deformable arm is ensured, and the arm portions are more easily deformed.
Control valve seat 75
As shown in fig. 6A, the control valve seat 75 includes: an outer seat portion 76 that holds the control valve 70; a back pressure flow passage 77 that forms a flow passage for oil that regulates the oil pressure in the back pressure chamber 68P (see fig. 4); and a low speed flow passage 78 that forms a flow passage for low speed oil.
As shown in fig. 4, the control valve seat 75 includes: a communication chamber 82 that communicates with the back pressure flow passage 77; a back pressure communication passage 83 that connects the communication chamber 82 with the back pressure chamber 68P; and a low-speed communication passage 85 that connects the low-speed flow passage 78 with the inflow flow passage 81.
The communication chamber 82 communicates with the back pressure port flow passage 84 on the second axially inner side, communicates with the back pressure flow passage 77 on the second axially outer side, and faces the back pressure communication passage 83 in the second radial direction.
The back pressure communication passage 83 communicates with the communication chamber 82 on the second radially inner side, and communicates with the back pressure chamber 68P on the second radially outer side.
The flow passage sectional area of the oil in the low speed communication passage 85 is larger than that of the oil in the low speed flow passage 78. In the first embodiment, the flow of oil at a low speed, which will be described later, is regulated in the low-speed flow passage 78. Therefore, the flow of oil is not throttled on the upstream side of the low-speed flow passage 78 in the flow of oil.
Throttle member 79-
As shown in fig. 4, the throttle member 79 includes a back pressure port flow passage 84, and the back pressure port flow passage 84 connects the inflow flow passage 81 and the communication chamber 82. The flow passage sectional area of the oil of the back pressure port flow passage 84 is smaller than the flow passage sectional area of the oil of the back pressure communication passage 83 and the back pressure flow passage 77. Further, the back pressure port flow passage 84 prevents oil in the back pressure chamber 68P from returning to the inflow flow passage 81.
- (communication portion 80)
As shown in fig. 3, the communication portion 80 according to the first embodiment includes: an inflow flow passage 81 through which oil from the communication passage L flows; and a connecting portion 89 connected to the control valve seat 75.
The inner diameter of the connecting portion 89 is substantially equal to the outer diameter of the second axially inner side of the control valve seat 75. Further, the second axially inner end of the control valve seat 75 is inserted into the connecting portion 89. The communication portion 80 may be configured to be inserted inside the control valve seat 75.
(connecting runner 90)
As shown in fig. 2, the connection flow path portion 90 includes: an inner flow passage 91 provided on the second radially inner side; and an outer flow passage 92 disposed on the second radially outer side.
The inner flow passage 91 communicates with the outer tubular body opening 12H on the second axially inner side, and communicates with the inflow flow passage 81 of the communicating portion 80 and the main flow passage 53 of the main valve seat 52 on the second axially outer side.
A plurality of outer flow passages 92 are provided in the first embodiment. The second axially inward side of the outer flow passage 92 communicates with the housing opening 13H, and the second axially outward side communicates with the housing inner flow passage 111.
(outer case 100C)
As shown in fig. 2, the outer case 100C is a substantially cylindrical member. The second axially inner side of the outer case 100C is fixed to the damper case 13 by, for example, welding or the like.
Further, the outer case 100C forms a case inner flow passage 111 on a second radially outer side of the main valve portion 50 and the damping force adjusting portion 60, and the case inner flow passage 111 is a flow passage for oil in the outer case 100C.
The oil flowing out of the second opening 67H2 of the lid 67 and the oil flowing out of the main flow passage 53 of the main valve seat 52 by opening the main valve 51 flow into the in-case flow passage 111.
[ adjustment operation of the damping force adjusting portion 60 ]
Next, the adjustment operation in the damping force adjusting portion 60 will be described.
As shown in fig. 4, the control valve 70 is pressed against the control valve seat 75 by pushing the pressing member 65 inward in the second axial direction. The pressing force of the pressing member 65 varies according to the amount of current flowing through the solenoid portion 62 (see fig. 2).
For example, in the damping force adjusting portion 60, a state is formed in which the pressing force of the pressing member 65 is maximized. At this time, the control valve 70 most strongly presses the control valve seat 75. At this time, the valve contact portion 651 of the pressing member 65 brings the second facing portion 72 close to the low-speed flow passage 78 and presses the second facing portion 72 against the low-speed flow passage 78 (low-speed flow passage circle 78R).
The second facing portion 72 according to the first embodiment is connected to the first facing portion 71 via the inner arm portion 73A. Therefore, as the valve contact portion 651 of the pressing member 65 moves the second facing portion 72, the first facing portion 71 approaches the back pressure flow passage 77. The first facing portion 71 (back pressure flow path circle 77R) presses the back pressure flow path 77. Here, in the first embodiment, the back pressure flow passage 77 protrudes higher than the low speed flow passage 78. Therefore, in the first embodiment, a state in which the back pressure flow passage 77 is more reliably pressed is formed by the first facing portion 71.
As described above, the first facing portion 71 contacts the back pressure flow path circle 77R, and the back pressure flow path 77 is closed. At the same time, the second facing portion 72 contacts the low speed flow passage circle 78R, and the low speed flow passage 78 is closed.
For example, in the damping force adjusting portion 60, a state is formed in which the pressing force of the pressing member 65 is minimized. At this time, in the damping force adjusting portion 60, the first facing portion 71 is separated from the back pressure flow path circle 77R, and the back pressure flow path 77 is opened. At the same time, the second facing portion 72 separates from the low speed flow passage circle 78R, and the low speed flow passage 78 opens.
For example, in the damping force adjusting portion 60, a state between a state in which the pressing force of the pressing member 65 is minimized and a state in which the pressing force is maximized is provided. In this state, in the damping force adjusting portion 60, the first facing portion 71 is farther from the back pressure flow path circle 77R than the state where the pressing force is the largest, and is closer to the back pressure flow path circle 77R than the state where the pressing force is the smallest. At the same time, the second facing portion 72 is farther from the low-speed flow path circle 78R than the state where the pressing force is the largest, and is closer to the low-speed flow path circle 78R than the state where the pressing force is the smallest.
In the first embodiment described above, the low-speed flow passage 78 has a lower projection height than the back pressure flow passage 77, and the second facing portion 72 facing the low-speed flow passage 78 is pushed by the pressing member 65. On the other hand, in the case where the protruding height of the back pressure flow passage 77 is lower than that of the low speed flow passage 78, the first facing portion 71 facing the lower back pressure flow passage 77 may be pushed by the pressing member 65.
Further, the valve contact portion 651 of the pressing member 65 may be brought into contact with both the first facing portion 71 and the second facing portion 72 to advance and retreat with respect to the low-speed flow passage 78 and the back-pressure flow passage 77.
[ operation of the Hydraulic shock absorber 1 ]
Fig. 7A and 7B are operation explanatory diagrams of the hydraulic shock absorber 1 according to the first embodiment. Incidentally, fig. 7A shows the flow of oil during the extension stroke, and fig. 7B shows the flow of oil during the compression stroke.
First, the operation of the hydraulic shock absorber 1 in the extension stroke will be described.
As shown in fig. 7A, during the extension stroke, the rod 20 moves to the other side with respect to the cylinder 11. At this time, the piston valve 32 is kept closed by the piston oil port 311. In addition, the volume of the second oil chamber Y2 decreases as the piston portion 30 moves toward the other side. Further, the oil in the second oil chamber Y2 flows out from the cylinder opening 11H to the communication passage L.
The oil flows into the outer damper portion 100 through the communication passage L and the outer tubular body opening portion 12H. Further, in the outer damper portion 100, first, oil flows into the inner flow passage 91 of the connection flow passage portion 90. Thereafter, in the outer damping portion 100, a damping force is generated in the main valve 51 or the control valve 70. Incidentally, the flow of oil at this time will be described in detail later.
Thereafter, the oil that has passed through the main valve 51 or the control valve 70 flows out into the in-case flow passage 111. Further, the oil flows from the housing opening portion 13H into the reservoir chamber R through the outer flow passage 92 of the connection flow passage portion 90.
The pressure of the first oil chamber Y1 is low relative to the pressure of the reservoir chamber R. Therefore, the oil in the reservoir chamber R flows into the first oil chamber Y1 through the bottom portion 40.
Next, the operation of the hydraulic shock absorber 1 during the compression stroke will be described.
As shown in fig. 7B, during the compression stroke, the rod 20 is relatively moved to one side with respect to the cylinder 11. In the piston section 30, the piston valve 32 that closes the piston oil passage opening 311 opens due to a pressure difference between the first oil chamber Y1 and the second oil chamber Y2. The oil in the first oil chamber Y1 flows out into the second oil chamber Y2 through the piston oil passage opening 311. Here, the rod 20 is placed in the second oil chamber Y2. Therefore, the oil flowing from the first oil chamber Y1 into the second oil chamber Y2 becomes excessive due to the volume of the rod 20. Therefore, the oil amount corresponding to the volume of the rod 20 flows out from the cylinder opening 11H to the communication passage L.
The oil flows into the outer damper portion 100 through the communication passage L and the outer tubular body opening portion 12H. Incidentally, the flow of oil in the outer damping portion 100 is the same as the flow of oil during the extension stroke described above. That is, in the hydraulic shock absorber 1 according to the first embodiment, the direction in which oil flows in the outer damping portion 100 is the same during the compression stroke and the extension stroke.
As described above, in the hydraulic shock absorber 1 according to the first embodiment, the damping force is generated in the outer damping portion 100 during both the compression stroke and the extension stroke.
Next, the flow of oil in the outer damping portion 100 according to the first embodiment will be described in detail.
First, the flow of oil in a state where the pressing force of the pressing member 65 is relatively small will be described. Hereinafter, an example of a state in which the control valve 70 is separated from the back pressure flow circle 77R and the low speed flow circle 78R will be described.
Fig. 8A and 8B are explanatory diagrams of the flow of oil in the outer damping portion 100 according to the first embodiment. Note that fig. 8A shows a low-speed flow of oil in a state where the pressing force of the pressing member 65 is relatively small, and fig. 8B shows a high-speed flow of oil in a state where the pressing force of the pressing member 65 is relatively small.
(Low speed)
As shown in fig. 8A, in the case where the moving speed of the piston portion 30 (see fig. 1) is low, the oil flowing into the inner flow passage 91 flows into the inflow flow passage 81 and the main flow passage 53. Here, since the moving speed of the piston portion 30 is low, the flow of oil for opening the main valve 51 is not generated in the main flow passage 53.
On the other hand, the oil that has flowed into the inflow channel 81 mainly flows in the order of the low-speed communication channel 85, the low-speed channel 78, the low-speed channel circle 78R, the outer opening portion 74 (see fig. 6A and 6B), the second opening portion 67H2, and the lid channel 67R. Then, the oil flows out from the in-case flow passage 111 to the reservoir chamber R.
As described above, when the moving speed of the piston portion 30 is low, the damping force is generated when the flow of oil is throttled by the gap between the low-speed flow passage circle 78R of the low-speed flow passage 78 and the control valve 70.
(high speed)
As shown in fig. 8B, in the case where the moving speed of the piston portion 30 (see fig. 1) is high, the oil flowing into the inner flow passage 91 flows into the inflow flow passage 81 and the main flow passage 53. The oil flowing into the main flow passage 53 opens the main valve 51 and flows out into the reservoir chamber R.
Even when the moving speed is high, as in the case of the low speed, the oil that has flowed into the inflow channel 81 flows into the in-case channel 111 while generating the pressure difference due to the flow rate being reduced by the gap between the low speed channel circle 78R (see fig. 6A and 6B) and the control valve 70, and further flows out into the reservoir chamber R.
As described above, when the moving speed of the piston portion 30 is high, the damping force is generated mainly by the flow of the oil in the main flow passage 53 of the main valve seat 52.
The oil that has flowed into the inflow channel 81 transmits the pressure to the back pressure chamber 68P through the back pressure port channel 84 and the back pressure communication channel 83. However, the back pressure flow passage 77 communicating with the back pressure chamber 68P is opened by the control valve 70. Therefore, the pressure of the back pressure chamber 68P is lower than that in the case where the control valve 70 is pressed against the back pressure flow passage 77. The main valve 51, which comes into contact with the back pressure generating mechanism 68, relatively easily opens the main flow passage 53. Therefore, in a state where the pressing force of the pressing member 65 is relatively small, the damping force generated by the flow of the oil in the main flow passage 53 that opens the main valve 51 is relatively small.
Next, the flow of oil in a state where the pressing force of the pressing member 65 is relatively large will be described.
Hereinafter, an example of a state in which the control valve 70 is pressed against the back pressure flow path circle 77R and the low speed flow path circle 78R will be described.
Fig. 9A and 9B are explanatory diagrams of the flow of oil in the outer damping portion 100 according to the first embodiment. Note that fig. 9A shows a low-speed flow of oil in a state where the pressing force of the pressing member 65 is relatively large, and fig. 9B shows a high-speed flow of oil in a state where the pressing force of the pressing member 65 is relatively large.
(Low speed)
As shown in fig. 9A, when the moving speed of the piston portion 30 is low, the oil flowing into the inner flow passage 91 flows into the inflow flow passage 81 and the main flow passage 53. Here, since the moving speed of the piston portion 30 is low, there is no flow of oil flowing through the main flow passage 53 by opening the main valve 51.
On the other hand, the oil that has flowed into the inflow channel 81 passes through the low-speed communication passage 85 and flows into the low-speed channel 78. Then, while the control valve 70 is opened, the oil flows through the low speed flow passage 78 and the low speed flow passage circle 78R (see fig. 6A and 6B). Further, the oil flows mainly in the order of the outer opening portion 74 (see fig. 6A and 6B), the second opening portion 67H2, and the lid flow passage 67R. Then, the oil flows out from the in-case flow passage 111 to the reservoir chamber R.
As described above, when the moving speed of the piston portion 30 (see fig. 1) is low, the damping force is generated by the oil flowing in the low-speed flow passage circle 78R of the control valve seat 75 while the control valve 70 is opened. The damping force when oil flows through the low-speed flow passage circle 78R is higher than that in the case where the control valve 70 is separated from the low-speed flow passage circle 78R.
(high speed)
As shown in fig. 9B, when the moving speed of the piston portion 30 is high, the oil flowing into the inner flow passage 91 flows into the inflow flow passage 81 and the main flow passage 53. The oil flowing into the main flow passage 53 opens the main valve 51 and flows out into the reservoir chamber R.
Even when the moving speed is high, the oil that has flowed into the inflow channel 81 flows into the in-case channel 111 while generating a pressure difference, and further flows out into the reservoir chamber R, because the flow rate is reduced by the gap between the low-speed channel circle 78R (see fig. 6A and 6B) and the control valve 70, similarly to when the pressing force of the pressing member 65 is comparatively small.
As described above, when the moving speed of the piston portion 30 is high, the damping force is generated mainly by the flow of the oil in the main flow passage 53 of the main valve seat 52.
The oil that has flowed into the inflow channel 81 transmits the pressure to the back pressure chamber 68P through the back pressure port channel 84 and the back pressure communication channel 83. The back pressure flow passage 77 communicating with the back pressure chamber 68P is in a state of being pressed by the control valve 70. Therefore, the pressure of the back pressure chamber 68P is higher than that in the case where the back pressure flow passage 77 is opened. Further, the main valve 51 in contact with the back pressure generating mechanism 68 is relatively difficult to open the main flow passage 53. Therefore, in a state where the pressing force of the pressing member 65 is relatively high, the damping force generated by the flow of oil in the main flow passage 53 that opens the main valve 51 is relatively large.
As described above, in the hydraulic shock absorber 1 according to the first embodiment, by operating the pressurizing member 65, both the low-speed damping force adjustment and the high-speed damping force adjustment are performed. That is, in the hydraulic shock absorber 1 according to the first embodiment, by changing the pressing force of the control valve 70 against the control valve seat 75 using the pressurizing member 65, the following are adjusted: a flow passage area of the low speed flow passage 78 which is a flow passage of oil at a low speed; and a flow passage area of the back pressure flow passage 77 in relation to a flow passage area of the oil at a high speed, wherein the back pressure flow passage 77 regulates the pressure of the back pressure chamber 68P.
In the hydraulic shock absorber 1 according to the first embodiment, the flow of oil in the back pressure flow passage 77 and the flow of oil in the low speed flow passage 78 can be simultaneously controlled by the single control valve 70. In particular, in the hydraulic shock absorber 1 according to the first embodiment, since the flow of low-speed oil in the low-speed flow passage 78 can be controlled, it is possible to perform adjustment when the main valve 51 opens the main flow passage 53 (so-called valve opening point), and it is possible to achieve finer control of damping than in the related art.
In the above-described operation example, two modes of the state where the pressing force of the pressing member 65 is relatively large and the state where the pressing force of the pressing member 65 is relatively small have been described, but the present invention is not limited to the above-described two modes. The pressing force of the pressing member 65 can be selectively set within a range in which the pressing force of the pressing member 65 can be adjusted according to the amount of current of the solenoid portion 62. With this setting, the damping force adjusting portion 60 according to the first embodiment can adjust the damping force at the low speed and the damping force at the high speed in multiple stages.
Next, the flow of oil when the solenoid portion 62 is in the non-energized state will be described.
Fig. 10A and 10B are explanatory diagrams of the flow of oil in the outer damping portion 100. Note that fig. 10A shows a low-speed oil flow when the solenoid portion 62 is in an unexcited state, and fig. 10B shows a high-speed oil flow when the solenoid portion 62 is in an unexcited state.
As shown in fig. 10A and 10B, when the solenoid portion 62 is in an unexcited state, the compression coil spring 63 pushes back the plug 64 toward the second axially outer side. Therefore, the pressing member 65 fixed to the plug 64 is in a state of being pressed against the lid portion 67.
(Low speed)
As shown in fig. 10A, in the case where the moving speed of the piston portion 30 is low, similarly to the flow of oil described with reference to fig. 8A, the oil that has flowed into the inflow channel 81 flows in the order of the low-speed communication channel 85, the low-speed channel 78, the low-speed channel circle 78R, the inner opening portion 73 or the outer opening portion 74 (see fig. 6A and 6B), the groove portion 653, and the cover channel 67R. Then, the oil flows out into the in-case flow passage 111.
Further, when the moving speed of the piston portion 30 is low, a damping force is generated by the flow of oil in the groove portion 653. In the first embodiment, the channel portion 653 has a smaller flow passage sectional area than the low-speed flow passage 78. Therefore, for example, the damping force generated by the flow of the oil in the groove portion 653 is larger than the damping force generated by the flow of the oil in the low-speed flow passage 78.
(high speed)
As shown in fig. 10B, in a state where the moving speed of the piston portion 30 is high, the oil that has flowed into the inner flow passage 91 flows into the inflow flow passage 81 and the main flow passage 53, similarly to the flow of the oil described with reference to fig. 8B. The oil that has flowed into the main flow passage 53 opens the main valve 51 and flows out into the in-casing flow passage 111.
Even when the moving speed is high, as in the case of a low speed, the oil that has flowed into the inflow channel 81 flows into the in-housing channel 111 while generating a pressure difference due to the flow rate being reduced by using the groove portion 653, and further flows out into the reservoir chamber R.
As described above, when the moving speed of the piston portion 30 is high, the damping force is generated mainly by the flow of the oil in the main flow passage 53 of the main valve seat 52.
Here, the oil that has flowed into the inflow channel 81 transmits the pressure to the back pressure chamber 68P through the back pressure port channel 84 and the back pressure communication channel 83. The back pressure chamber 68P communicates with the in-case flow passage 111 via the back pressure flow passage 77. Here, the flow of oil between the back pressure chamber 68P and the in-case flow passage 111 needs to pass through the groove 653. When the flow of oil is throttled by the groove 653, the outflow of oil from the back pressure chamber 68P is suppressed, and the pressure of the back pressure chamber 68P is maintained relatively high. Further, the main valve 51 that comes into contact with the partition wall member 681 is relatively difficult to open the main flow passage 53. Therefore, when the solenoid portion 62 is in the non-excited state, the damping force generated by the flow of the oil in the main flow passage 53 that opens the main valve 51 is larger.
As described above, in the hydraulic shock absorber 1 according to the first embodiment, even when the solenoid portion 62 is not energized, both the damping force at low speed and the damping force at high speed are made relatively high.
Next, the damping force generated by the main valve portion 50 according to the first embodiment will be described in detail.
Fig. 11 is an explanatory diagram of the damping force characteristic of the main valve portion 50 according to the first embodiment.
The main valve seat 52 includes a center seat 520, an inner seat 521, and an outer seat 522 (see fig. 4 and 5). Further, a groove portion 521T is provided in the inner seat portion 521. Therefore, the oil flowing through the main flow passage 53 provided at the second radially inner side of the inner seat portion 521 flows first between the center seat portion 520 and the inner seat portion 521. Further, the oil flows between the inner seat portion 521 and the outer seat portion 522 through the groove portion 521T. At this time, the main valve 51 comes into contact with both the inner seat portion 521 and the outer seat portion 522 (hereinafter, also referred to as a first state).
Thereafter, after the first state, oil is accumulated between the inner seat portion 521 and the outer seat portion 522, so that the main valve 51 is separated from the outer seat portion 522 (hereinafter, referred to as a second state). At this time, the flow passage sectional area of the oil between the main valve 51 and the outer seat portion 522 is smaller than the flow passage sectional area of the oil in the groove portion 521T. Thus, in the second state, a damping force having an orifice characteristic is exhibited.
Thereafter, when the flow rate increases and oil flows from the main flow passage 53, the main valve 51 separates from the inner seat 521 (hereinafter, referred to as a third state). At this time, the flow passage sectional area of the oil between the main valve 51 and the outer seat portion 522 is equal to or larger than the flow passage sectional area of the oil in the groove portion 521T.
As shown in fig. 11, the damping force characteristic of the main valve portion 50 according to the first embodiment is as follows. The first state is a state from a state in which the main valve 51 is in contact with both the inner seat 521 and the outer seat 222 to a state in which a slight gap is generated between the main valve 51 and the outer seat 522. That is, the first state is a state in which only a slight outflow occurs from a state in which no oil flows out to the outside. Therefore, the damping force generated in the first state is minimal.
In the second state where the main valve 51 is brought into contact with the inner seat portion 521 and is separated from the outer seat portion 522, the pressure receiving area of the main valve 51 extends from the center seat portion 520 to the outer seat portion 522 in the second radial direction (see fig. 4). Therefore, the damping force generated in the second state is higher than the damping force generated in the first state and lower than the damping force generated in the third state. In addition, the amount of change in the damping force corresponding to the flow rate is smaller in the second state than in the first state and the third state.
In the third state where the main valve 51 is separated from both the inner seat portion 521 and the outer seat portion 522, the pressure receiving area of the main valve 51 extends from the center seat portion 520 to the inner seat portion 521 in the second radial direction (see fig. 4). Therefore, the damping force generated in the third state is higher than the damping forces generated in the first and second states. In addition, in the third state, the amount of change in the damping force corresponding to the flow rate is smaller than in the first state and larger than in the second state.
As described above, in the main valve 50 according to the first embodiment, by using one main valve 51 for at least one main valve seat 52, the damping force characteristic that changes the damping force in stages according to the flow rate is realized.
In particular, in the main valve portion 50 according to the first embodiment, the above-described damping force characteristic is achieved by the main valve 51 and the main valve seat 52 having a relatively simple structure.
Next, a method of manufacturing the hydraulic shock absorber 1 according to the first embodiment will be described. The assembling method of the outer damping portion 100 according to the first embodiment will be described in detail below.
As shown in fig. 3, when assembling the outer damping portion 100 according to the first embodiment, first, the cover portion 67 is prepared. Then, the plug 64 to which the pressing member 65 is attached is inserted from the first opening portion 67H1 side of the cover portion 67, and passes through the second opening portion 67H 2. Then, the compression coil spring 63 is fitted into the pressing member 65. The control valve 70, the control valve seat 75, and the orifice member 79 are inserted in this order from the first opening portion 67H1 side of the lid portion 67. In the first embodiment, the control valve seat 75 is inserted into the lid portion 67.
The communication portion 80 is inserted from the first opening portion 67H1 side of the cover portion 67, and the second axially inward end portion of the control valve seat 75 is inserted into the connecting portion 89. Then, the washer member 684 and the return spring 683 are attached to the communication portion 80. The seal member 682, the partition wall member 681, and the main valve 51 are inserted in this order from the first opening portion 67H1 side of the cover portion 67, and these members are attached. Then, the main valve seat 52 is inserted from the first opening portion 67H1 side of the lid portion 67, and the communication portion 80 is inserted into the opening portion 52H of the main valve seat 52.
As described above, the main valve portion 50 and the damping force adjusting portion 60 are combined together by accommodating various components inside the cap portion 67.
Various components housed inside the cap portion 67 can be held in the cap portion 67 by pressing the second axially inward end portion of the cap portion 67, by screwing the main valve seat 52 to the cap portion 67, or by press-fitting the main valve seat 52 into the cap portion 67.
Further, as shown in fig. 2, the main valve portion 50 and the damping force adjusting portion 60 combined together by the lid portion 67, and the connection flow path portion 90 are sequentially inserted from the second axial outer side of the outer case 100C. Further, the solenoid case 60C is inserted from the second axial outer side of the outer case 100C, and the solenoid case 60C is fixed to the outer case 100C by bolt fastening, press fitting, or the like. Then, by fitting the solenoid portion 62 into the solenoid case 60C, the assembly of the outer damping portion 100 is completed.
The outer damper portion 100 that has been assembled is attached so that the connection flow path portion 90 penetrates the outer connection portion 12J of the outer tubular body 12, and is fixed to the damper housing 13 by welding or the like, for example.
As described above, in the hydraulic shock absorber 1 according to the first embodiment, the main valve 51 constituting the main valve portion 50 and the control valve 70 constituting the damping force adjusting portion 60 are housed inside the cap portion 67. In this way, by adopting a configuration in which the main valve 51 and the control valve 70 are collectively accommodated in one cap portion 67, the cap portion 67 can be handled as one unit, so that the ease of assembly of the hydraulic shock absorber 1 can be improved.
< first modification >
Next, the hydraulic shock absorber 1 to which the first modification is applied will be described.
Fig. 12A and 12B are explanatory diagrams of the hydraulic shock absorber 1 according to the first modification. Note that fig. 12A is a partial sectional view of the main valve portion 50 and the damping force adjustment portion 60 according to the first modification, and fig. 12B is a top view of the sealing member 682 according to the first modification.
As shown in fig. 12A, the outer damping portion 100 according to the first modification includes a seal member 1682 in place of the seal member 682.
The seal member 1682 is similar in basic construction to the seal member 682. However, the seal member 1682 has a plurality of projections 682P (an example of projections) projecting from the inner circumferential surface 682N toward the second radially inner side. A plurality of the projections 682P are provided at substantially equal intervals in the circumferential direction of the seal member 1682.
Further, as shown in fig. 12B, the seal member 1682 is disposed such that the projection 682P comes into contact with the first surface S1 of the partition wall member 681.
As described with reference to fig. 4, in the outer damping portion 100, the clearance C2 is provided between the seal member 1682 and the partition wall member 681 so that the seal member 1682 is pressed against the inner periphery of the cover portion 67. However, the partition wall member 681 also has a clearance C1 with respect to the cap 67, so that even when one side of the main valve 51 floats and the partition wall member 681 is inclined together with the main valve 51, the occurrence of biting or the like with respect to the cap 67 is prevented. Therefore, the partition wall member 681 can also move in the second radial direction. Therefore, in the outer damping portion 100 according to the first modification, the partition wall member 681 is positioned on the second radial direction inner side by the projection 682P of the seal member 1682.
< second modification >
Next, the hydraulic shock absorber 1 to which the second modification is applied will be described.
Fig. 13 is an explanatory diagram of a hydraulic damper 1 according to a second modification.
As shown in fig. 13, the outer damping portion 100 according to the second modification includes a return spring 1683 instead of the return spring 683.
The basic construction of return spring 1683 is the same as return spring 683. However, in the return spring 1683, the position where the annular portion 683R is fixed by the washer member 684 and the position where the arm portion 683A comes into contact with the seal member 682 are substantially the same in the second axial direction.
In the outer damping portion 100 according to the second modification, when the main valve 51 deforms and moves to the second outer side, the elastic force of the return spring 1683 acts on the seal member 682 and the partition wall member 681. Therefore, in the hydraulic shock absorber 1 according to the second modification, the return spring 1683 is not always maintained in the deformed state, but is deformed only when the main valve 51 is operated. Further, in the outer damper portion 100 according to the second modification, plastic deformation of the return spring 1683 is suppressed.
< second embodiment >
Next, the hydraulic shock absorber 1 according to the second embodiment will be described.
Fig. 14 is a sectional view of an outer damping portion 200 according to a second embodiment.
Fig. 15 is a partial sectional view of a main valve portion 250 and a damping force adjusting portion 260 according to the second embodiment.
Fig. 16 is an explanatory diagram of the main valve seat 55 according to the second embodiment.
Fig. 17 is an explanatory diagram of a back pressure generating mechanism 69 according to the second embodiment.
In the description of the second embodiment, the same configurations as those of the first embodiment are given the same reference numerals, and detailed description thereof will be omitted.
As shown in fig. 14, the outer damping portion 200 includes: a main valve portion 250 that generates a damping force mainly in the hydraulic shock absorber 1 according to the second embodiment; and a damping force adjusting part 260 that adjusts the magnitude of the damping force generated by the outer damping part 200. Further, the outer damping portion 200 includes: a connection flow passage portion 90 that forms a flow passage of oil from the communication passage L for the main valve portion 250; and an outer case 100C that accommodates various components constituting the outer damping portion 200.
(Main valve portion 250)
As shown in fig. 15, the main valve portion 250 includes: a main valve 51 that generates a damping force by controlling the flow of oil to be throttled; and a main valve seat 55 facing the main valve 51 and making contact with the main valve 51.
As shown in fig. 16, the main valve seat 55 is a columnar member having an opening 55H on the second radial direction inner side. An inflow portion 281 of a control valve seat 275, which will be described later, is inserted into a portion of the opening portion 55H of the main valve seat 55 (see fig. 15).
As shown in fig. 16, the main valve seat 55 includes a center seat portion 550 around the opening portion 55H. The main valve seat 55 includes: an inner seat 551, disposed on a second radially outer side of the central seat 550; and an outer seat portion 552 disposed second radially outward of each inner seat portion 551. Further, the main valve seat 55 has a common portion 553 on a second radially outer side of the center seat portion 550 and a second radially inner side of each inner seat portion 551.
Further, the main valve seat 55 includes a main flow passage 53 penetrating in the second axial direction on the second radial direction outer side of the opening portion 55H.
The center seat 550 is formed in an arc shape. The center seat 550 protrudes from the port hole 532 toward the main valve 51 (second axially outward in the present embodiment). Furthermore, a second radially inner portion of main valve 51 faces central seat 550.
The inner seat 551 is formed in an arc shape. The inner seat 551 protrudes from the port hole 532 toward the main valve 51. In addition, in the second embodiment, the protruding height of the inner seating portion 551 is substantially equal to the protruding height of the central seating portion 550 and the outer seating portion 552.
The outer seat portion 552 is formed in a U shape. The outer seat portion 552 protrudes from the port opening 532 toward the main valve 51 side. In the main valve seat 55 according to the second embodiment, the inner seat portion 551 is connected with the outer seat portion 552.
The common portion 553 (an example of the common portion) protrudes straight toward the main valve 51 side. In addition, each common portion 553 extends substantially parallel to the second radial direction. The common portion 553 is connected to the connection between the central seat portion 550, the inner seat portion 551 and the outer seat portion 552. Further, the common portion 553 is common to the inner seat portion 551 and the outer seat portion 552, and forms a portion that comes into contact with the main valve 51.
In the main valve seat 55 according to the second embodiment, each common portion 553 includes a groove portion 553T (an example of a circulation portion). The flow passage cross-sectional area of each groove 553T is formed to be relatively small. That is, the groove portions 553T constitute so-called orifice flow passages. Each groove 553T allows oil from main flow passage 53 flowing between center seat portion 550 and inner seat portion 551 to flow between center seat portion 550 and outer seat portion 552 in a state where main valve 51 is in contact with common portion 553.
As shown in fig. 15, the main flow passage 53 forms a parallel flow passage with respect to the back pressure flow passage 77 and the low speed flow passage 78 of the control valve seat 275. In addition, a plurality of main flow passages 53 according to the second embodiment are provided. The second axially inner flow channel port 531 of each main flow channel 53 communicates with the opening 55H and faces the connecting flow channel portion 90. Further, a second axially outer flow port 532 of each main flow passage 53 is located between the center seat 550 and the inner seat 551 (see fig. 16).
In the main valve portion 250 according to the second embodiment configured as described above, similarly to the main valve portion 50 according to the first embodiment, a damping force characteristic in which the damping force is changed stepwise according to the flow rate is realized.
(damping force adjusting part 260)
As shown in fig. 15, the damping force adjusting portion 260 includes: an advancing-retreating portion 261 that advances and retreats the control valve 70 relative to the control valve seat 275; and a back pressure generating mechanism 69 that changes the ease of deformation of the main valve 51 with respect to the main valve seat 55. The damping force adjusting portion 260 includes a cover portion 267 that covers various components such as the main valve portion 50, the control valve 70, and the control valve seat 275. Further, the damping force adjusting portion 260 includes a valve holding member 367, and the valve holding member 367 supports the control valve 70 at a second axial outer side of the control valve 70.
The basic configuration of the damping-force adjusting portion 260 according to the second embodiment is the same as that of the damping-force adjusting portion 60 according to the first embodiment. However, the cover portion 267 of the damping force adjusting portion 260 according to the second embodiment is different from the cover portion 67 according to the first embodiment.
As shown in fig. 14, the cover portion 267 (an example of the accommodating portion) according to the second embodiment includes: a first opening portion 267H1 formed on the second axially inner side; a second opening portion 267H2 formed axially outward of the first opening portion 267H 1; and a third opening portion 267H3 formed axially outward of the second opening portion 267H 2. Further, the cover 267 includes: a first cover 2671 which is a portion from the first opening portion 267H1 to the second opening portion 267H2 in the second axial direction; and a second lid 2672 that is a portion from the second opening portion 267H2 to the third opening portion 267H3 in the second axial direction.
The first cover 2671 is formed in a substantially cylindrical shape. The first inner diameter of the first opening portion 267H1 is larger than the second inner diameter of the second opening portion 267H 2. Further, a plurality of inner diameter portions having different inner diameters are formed inside the first cover portion 2671, respectively. In the first lid 2671, an inner diameter portion provided on the second axial inner side among the plurality of inner diameter portions is formed to have a larger inner diameter than an inner diameter portion provided on the second axial outer side. Further, the first cover portion 2671 accommodates at least the main valve 51 (an example of a valve) and the control valve 70 (an example of a back pressure control valve) of the main valve portion 250.
The second cover 2672 (an example of an expansion receiving portion) is formed in a substantially cylindrical shape. The third inner diameter of the third opening portion 267H3 is larger than the second inner diameter of the second opening portion 267H 2. The second cover 2672 is formed to expand from the first cover 2671 by extending axially outward from the second opening 267H 2. Further, the second cap portion 2672 accommodates the solenoid portion 62 (an example of an operating portion) and the plug 64.
The lid portion 267 according to the second embodiment configured as described above is not constituted by a plurality of divided members, but individually accommodates the solenoid portion 62, the plug 64, the main valve 51 of the main valve portion 250, and the control valve 70.
In addition, a part of the lid portion 267 according to the second embodiment forms the back pressure chamber 68P together with the back pressure generating mechanism 69 and the control valve seat 275.
Also, in the second embodiment, by collectively housing the main valve 51 and the control valve 70 in the single lid portion 267, it is possible to perform handling in units of the lid portion 267, so that it is possible to improve the ease of assembly of the hydraulic shock absorber 1.
The pressing member 65 according to the second embodiment includes the groove 653. The groove 653 according to the second embodiment enables oil to flow between the pressing member 65 and the valve holding mechanism 367 or the cap 267 in a state where the pressing member 65 moves axially outward in the second axial direction and contacts the valve holding member 367 or the cap 267 when the solenoid portion 62 is in the non-energized state.
Also in the second embodiment, a groove portion or a through hole may be provided in the valve holding member 367 or the cap portion 267 so that oil flows between the valve holding member 367 or the cap portion 267 and the pressing member 65 when the solenoid portion 62 is in the non-energized state.
Back pressure generating means 69
As shown in fig. 15, the back pressure generating mechanism 69 includes: a contact member 691 provided on the opposite side (second axially outer side) of the main valve seat 55 with respect to the main valve 51; and a sealing member 692 that seals between the cover 267 and the contact member 691. Further, the back pressure generating mechanism 69 includes: a return spring 693 that applies a force to the contact member 691 and the seal member 692 to press the contact member 691 and the seal member 692 toward the main valve 51; and a washer portion 694 interposed between the return spring 693 and the control valve seat 275.
As shown in fig. 17, the contact member 691 is an elastic member made of metal such as iron. The contact member 691 includes an inner ring portion 691U formed annularly at the second radial direction inner side and an outer ring portion 691S formed annularly at the second radial direction outer side of the inner ring portion 691U. Further, the contact member 691 includes: a connection portion 691J extending in the second radial direction and connecting the inner ring portion 691U and the outer ring portion 691S; and a main valve contact part 691V which contacts the main valve 51. The contact member 691 according to the second embodiment is a member integrally formed in a plate shape.
As shown in fig. 15, an inflow portion 281 (described later) of the control valve seat 275 is inserted into an inner ring portion 691U. Further, the inner ring portion 691U is interposed and fixed between the washer part 694 and the main valve 51.
The seal member 692 contacts the outer ring portion 691S in the second axially outer side.
The main valve contact part 691V is provided at a position corresponding to the outer ring part 691S in the contact member 691. The main valve contact part 691V annularly projects toward the main valve 51. The main valve contact portion 691V according to the second embodiment contacts the main valve 51 on the second radially outer side of the facing portion of the inner seat portion 551 and the second radially inner side of the facing portion of the outer seat portion 552.
As shown in fig. 17, the seal member 692 is formed in an annular shape. In addition, an elastically deformable resin material such as engineering plastic or rubber can be used for the sealing member 692. Then, as shown in fig. 15, the sealing member 692 seals between the contact member 691 and the cover 267. More specifically, the outer peripheral surface 692G of the seal member 692 contacts the inner periphery of the cover portion 267. The second axially inward first end surface 692T1 of the seal member 692 makes contact with the outer ring portion 691S of the contact member 691. Therefore, the seal member 692 prevents the oil in the back pressure chamber 68P from flowing out of the back pressure chamber 68P through the gap between the contact member 691 and the lid 267.
As shown in fig. 17, the seal member 692 according to the second embodiment includes a recess 69K (an example of a liquid reservoir) on the second axially inward first end face 692T1 and on the second axially outward second end face 692T 2. The concave portion 69K has: a first recess K1 formed in an annular shape of the seal member 692; and second recessed portions K2 formed linearly from the second radial outer side toward the first recessed portions K1, respectively.
Here, the high oil pressure in the back pressure chamber 68P is applied to the second end face 692T2 of the seal member 692. On the other hand, a lower oil pressure than the oil pressure of the back pressure chamber 68P is applied to the first end surface 692T1 of the seal member 692. Further, by providing the recess 69K in the first end face 692T1, the area of the first end face 692T1 to which the low oil pressure of the seal member 692 according to the second embodiment is applied is larger than the case where the recess 69K is not provided. As a result, the pressing force of the sealing member 692 against the contact member 691 increases due to the oil pressure difference between the first end surface 692T1 side and the second end surface 692T2 side.
Although the seal member 692 according to the second embodiment has the concave portion 69K on the second end face 692T2 that does not contact the contact member 691, the concave portion 69K of the second end face 692T2 is not an essential configuration for generating the above-described pressure difference. However, by providing the recess 69K in both the first end face 692T1 and the second end face 692T2, it is possible to perform attachment without considering the orientation of the sealing member 692 with respect to the contact member 691 when assembling the hydraulic shock absorber 1.
In the second embodiment, the oil flows between the seal member 692 and the contact member 691 by providing the recess 69K in the seal member 692, but the invention is not limited thereto. For example, the contact member 691 (an example of a back pressure chamber forming portion) may have a groove portion (an example of a reservoir) into which the oil flows into an end surface on the second outer side, that is, the side facing the seal member 692. Even in this case, the pressing force of the sealing member 692 against the contact member 691 increases due to the oil pressure difference between the first end surface 692T1 side and the second end surface 692T2 side.
As shown in fig. 17, the return spring 693 (an example of an elastic member) includes a ring-shaped portion 693R (an example of a ring-shaped portion) formed in a ring shape on the second radially outer side and a plurality of arm portions 693A extending from the ring-shaped portion 693R toward the second radially inner side. In addition, an elastic member such as metal can be used as a material of the return spring 693.
The end portion of the arm portion 693A on the second radially inner side is supported by the washer part 694. The annular portion 693R contacts the seal member 692 on the second axially outer side.
In the second embodiment, the arm portion 693A of the return spring 693 presses the seal member 692 against the lid portion 267 due to a component of the force in the second radial direction. As a result, also in the second embodiment, the sealing performance between the sealing member 692 and the cover 267 is improved.
Control valve seat 275-
As shown in fig. 15, the basic configuration of the control valve seat 275 according to the second embodiment is the same as that of the control valve seat 75 according to the first embodiment. However, the control valve seat 275 according to the second embodiment integrally has the functions of the throttling member 79 and the communicating portion 80 according to the first embodiment.
The control valve seat 275 according to the second embodiment includes the outer seat portion 76, the back pressure flow passage 77, and the low speed flow passage 78. In the control valve seat 275 according to the second embodiment, the position in the second radial direction between the back pressure flow passage 77 and the low speed flow passage 78 is opposite with respect to the control valve seat 75 according to the first embodiment. In addition, according to this positional relationship, also with respect to the functions of the first facing portion 71 and the second facing portion 72 in the control valve 70, the control valve 70 according to the second embodiment has the reverse relationship to the control valve 70 according to the first embodiment.
The control valve seat 275 according to the second embodiment includes: an inflow portion 281 through which oil flows from the communication passage L; and a first back pressure communication passage 283 connecting the inflow portion 281 and the back pressure chamber 68P. The control valve seat 275 includes: a throttle portion 279 that is provided in the first back pressure communication passage 283 and throttles the flow of oil; and a second back pressure communication passage 285 connecting the back pressure chamber 68P and the back pressure flow passage 77.
The inflow portion 281 communicates with the opening portion 55H of the main valve seat 55 on the second axially inner side, and communicates with the low-speed flow passage 78 on the second axially outer side.
The first back pressure communication passage 283 communicates with the inflow portion 281 on the second radial inner side, and communicates with the back pressure chamber 68P on the second radial outer side.
The flow passage sectional area of the oil of the throttle portion 279 is smaller than the flow passage sectional areas of the oil of the first back pressure communication passage 283 and the back pressure flow passage 77. Further, the throttle portion 279 prevents oil in the back pressure chamber 68P from returning to the inflow portion 281.
The second back pressure communication passage 285 communicates with the back pressure chamber 68P on the second axially inner side, and communicates with the low speed flow passage 78 on the second axially outer side.
In the hydraulic shock absorber 1 according to the second embodiment constructed as described above, by operating the pressurizing member 65, the adjustment of the damping force at the low speed and the adjustment of the damping force at the high speed can be performed.
< third modification >
Next, the hydraulic shock absorber 1 to which the third modification is applied will be described.
Fig. 18 is an explanatory diagram of a hydraulic damper 1 according to a third modification.
The outer damping portion 200 according to the third modification differs from the above-described example in that the contact member 691 according to the second embodiment is not provided.
As shown in fig. 18, the seal member 692 according to the third modification directly comes into contact with the main valve 51. In the third modification, the sealing member 692 also functions as the contact member 691 (an example of the back pressure chamber forming portion), and therefore, the sealing member 692 itself functions as a main member that forms the back pressure chamber 68P.
The return spring 693 makes contact with a corner of the seal member 692 on a second radially inner side and a second axially outer side. The return spring 693 applies a component of force in the second axial direction and a component of force in the second radial direction to the seal part 692. As a result, the sealing member 692 presses against the inner periphery of the lid portion 267, and also presses against the main valve 51.
In the third modification configured as described above, for example, the number of components can be reduced as compared with the back pressure generating mechanism 69 according to the second embodiment.
In the first embodiment, the second embodiment, the first modification, the second modification, and the third modification, the piston portion 30 and the bottom portion 40 are not limited to the structures shown in the above embodiments, and may have other shapes and other configurations as long as they function as a damping mechanism.
In addition, the respective constituent portions described in the first embodiment, the second embodiment, the first modification, the second modification, and the third modification may be combined and interchanged with each other.
The function of the outer damping portion 100 provided outside the cylinder 11 may be provided in the piston portion 30 or the like inside the cylinder 11. Similarly, the function of the outer damping portion 100 provided outside the cylinder 11 may be provided in the bottom portion 40 or the like. The hydraulic shock absorbers 1 according to the first embodiment, the second embodiment, the first modification, the second modification, and the third modification are not limited to so-called triple tube structures in which the cylinder 11, the outer tubular body 12, and the damper housing 13 are respectively formed in a tube shape, but the hydraulic shock absorbers 1 may have so-called double tube structures formed by the cylinder 11 and the damper housing 13.

Claims (5)

1. A damping-force generating mechanism comprising:
a valve configured to control a flow of a liquid within a flow passage through which the liquid flows,
a flow passage forming part including:
a first seat that is provided radially outside a flow passage port of the flow passage, protrudes from the flow passage port, and contacts the valve;
a second seat disposed radially outward of the first seat, protruding from the flow passage port, and contacting the valve; and
a circulation portion having an orifice that enables the liquid to flow from the flow port toward the second seat in a state where the valve is in contact with the first seat; and
a back pressure chamber forming portion that forms a back pressure chamber for applying back pressure to the valve and includes a contact portion that contacts the valve radially inward of a position of the second seat portion.
2. The damping-force generating mechanism according to claim 1,
wherein the first seat portion and the second seat portion are annular in shape, and
wherein the circulating part is provided in the first seat part.
3. A damping-force generating mechanism comprising:
a valve configured to control a flow of a liquid within a flow passage through which the liquid flows, an
A flow passage forming part including:
a first seat that is provided radially outside a flow passage port of the flow passage, protrudes from the flow passage port, and contacts the valve;
a second seat disposed radially outward of the first seat, protruding from the flow passage port, and contacting the valve;
a common portion that is used in common by the first seat portion and the second seat portion and that forms a portion that contacts the valve; and
a circulation portion having an orifice that enables the liquid to flow from the flow passage port toward the second seat in a state where the valve is in contact with the first seat, the circulation portion being provided in the common portion.
4. The damping-force generating mechanism according to any one of claims 1 to 3, further comprising:
another flow passage forming part which forms another flow passage arranged in parallel with the flow passage; and
a second valve configured to control a flow of the liquid in the other flow passage.
5. A pressure shock absorber, comprising:
a cylinder containing a liquid;
a piston portion that is connected to a rod that is movable in an axial direction, and that is movable in the cylinder body;
a valve configured to control a flow of the liquid within a flow passage through which the liquid flows according to a movement of the piston portion,
a flow passage forming part including:
a first seat that is provided radially outside a flow passage port of the flow passage, protrudes from the flow passage port, and contacts the valve;
a second seat disposed radially outward of the first seat, protruding from the flow passage port, and contacting the valve; and
a circulation portion having an orifice that enables the liquid to flow from the flow port toward the second seat in a state where the valve is in contact with the first seat, and
a back pressure chamber forming portion that forms a back pressure chamber for applying back pressure to the valve and includes a contact portion that contacts the valve radially inward of a position of the second seat portion.
CN201980027719.5A 2018-06-13 2019-04-22 Damping force generating mechanism and pressure shock absorber Active CN112041585B (en)

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JPWO2019239719A1 (en) 2020-06-25
WO2019239719A1 (en) 2019-12-19
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JP6719035B2 (en) 2020-07-08
DE112019001540T5 (en) 2020-12-10
CN112105835B (en) 2022-03-08
US20210054902A1 (en) 2021-02-25
WO2019239718A1 (en) 2019-12-19
CN112105835A (en) 2020-12-18
CN112041585A (en) 2020-12-04
JPWO2019239720A1 (en) 2020-06-25
WO2019239720A1 (en) 2019-12-19
US11761509B2 (en) 2023-09-19
US20220412427A1 (en) 2022-12-29
US20210033163A1 (en) 2021-02-04
CN112041586B (en) 2021-11-26
JP6735429B2 (en) 2020-08-05
US20210102595A1 (en) 2021-04-08
JPWO2019239718A1 (en) 2020-06-25
CN112041586A (en) 2020-12-04
US11603900B2 (en) 2023-03-14
JPWO2019239521A1 (en) 2020-07-02
WO2019239521A1 (en) 2019-12-19
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US11466747B2 (en) 2022-10-11
DE112019001541T5 (en) 2020-12-10

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